US20090291799A1 - Clutch - Google Patents
Clutch Download PDFInfo
- Publication number
- US20090291799A1 US20090291799A1 US12/470,045 US47004509A US2009291799A1 US 20090291799 A1 US20090291799 A1 US 20090291799A1 US 47004509 A US47004509 A US 47004509A US 2009291799 A1 US2009291799 A1 US 2009291799A1
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- US
- United States
- Prior art keywords
- clutching
- gear
- output device
- planet carrier
- speed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000008878 coupling Effects 0.000 claims description 8
- 238000010168 coupling process Methods 0.000 claims description 8
- 238000005859 coupling reaction Methods 0.000 claims description 8
- 238000001816 cooling Methods 0.000 claims description 4
- 238000009966 trimming Methods 0.000 abstract description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 125000006850 spacer group Chemical group 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
Definitions
- This invention relates to power transmission devices and, more particularly, to clutching devices that can achieve torque modulation and/or speed trimming, by manipulating only a fraction of torque transferred, but over a wider speed range.
- a clutching/speed-trimming device that is used to connect or disconnect a prime mover to or from the rest of a powertrain and/or auxiliary devices. It is also often important to be able to continuously change the speed-ratio between the prime-mover and the driven equipment, whether they are main propulsion or powertrain devices, or auxiliary devices such as, but not limited to, cooling fans, pumps, compressors and the like. Ideally, the speed ratio can be changed while the system is running and without interrupting the torque path. These functions are particularly important, but not limited to, applications where an internal combustion engine is the prime mover.
- the process of connecting the torque path is typically referred to as “clutching” while the process of interrupting the torque path is typically referred to as “de clutching.”
- the process of changing the speed ratio between the prime mover and auxiliary devices may be referred to as “speed trimming” or “speed modulation.”
- clutch modulation Energy from clutch modulation in traditional clutching devices is converted into heat, which is typically released into the atmosphere.
- Traditional clutches therefore have limited modulating capacity and/or, in the case of hydraulic systems, rather low operating efficiency.
- typically two clutching devices are used: a hydraulic unit to provide for modulation, and a friction unit to achieve full clutch engagement (e.g. lock-up torque converters) once the driven equipment is sped-up.
- clutching devices modulate the entire working torque over a speed range equal to the difference between the speed of the prime mover and the starting speed of the process machine. Therefore, clutches have a tendency of being rather large and it is difficult to achieve and automate smooth, repeatable modulation. This is especially true with friction-based clutches because coefficient of friction may change during the modulation.
- a clutching device that is smaller and more cost-effective than conventional, friction-based clutches.
- a clutching device capable of providing smooth, repeatable modulation, unrestricted in duration, and easy to automate regardless of operating conditions.
- a clutching device capable of converting the energy of clutch modulation into an energy form that can be readily recovered and/or reintroduced into the system to provide improved efficiency of the system even when the clutch is modulating for extended periods of time.
- the invention provides a clutching device that includes a planetary gear set connected to a prime mover.
- the planetary gear set includes a ring gear, a planet carrier with at least one planet and one sun gear disposed in the planet carrier the said planet gear engaged at one side with the ring gear, and at the other side with the sun gear.
- the device further includes a modulating device connected to the sun gear, and an output device connected to the planet carrier. Speed modulation between the prime mover and the output device is controlled by controlling the speed of rotation of the sun gear. Energy from the speed modulation is recoverable by the modulating device.
- FIG. 1 is a cut-out, partially exploded view of a clutching device according to one embodiment of the invention (modulating device not shown);
- FIG. 2 is an exploded view of the embodiment shown in FIG. 1 (modulating device shown).
- clutching devices for driving auxiliary equipment. It will be appreciated, however, that the clutching devices and underlying principals described herein can be applied in a variety of different industrial, marine, and other applications including the main drive of propulsion systems.
- FIGS. 1 and 2 show a clutching device according to one embodiment of the present invention.
- Clutching device 100 has a cover 14 connected to the front-end of an engine crankshaft (not shown) by means of an adapter (also not shown).
- Cover 14 is the input of clutching device 100 , and is connected to ring gear 1 .
- Ring gear 1 is engaged with planet gears 3 .
- Planet gears 3 are mounted in planet carrier 2 by means of bearings 5 and pins 4 , and are also engaged with sun gear 12 .
- An output device 15 is rigidly connected to planet carrier 2 and is the output of the assembly.
- Output device 15 may, for example, be a sheave or a sprocket.
- Output device 15 drives auxiliary equipment such as cooling fans, generators, pumps, compressors and the like. Where output device 15 drives the main drive of propulsion systems, output device 15 may be a shaft, for example.
- Sun gear 12 is connected to a modulating device 24 used to provide the control (reaction) torque for torque modulation.
- Modulating device 24 may, for example, be a hydraulic pump, a hydraulic motor, an electrical generator, an electrical motor, a friction clutch, a hydraulic coupling device, a magnetic coupling device, or the like.
- Rotational power of the crankshaft is transferred to output device 15 such that in operation, the correlation of the rotational speeds of cover 14 , sun gear 12 and output device 15 satisfy the following equation:
- N ring and N sun are the numbers of teeth on ring gear 1 and sun gear 12 , respectively, and W in , W out and W sun are the rotational speeds of cover 14 , output device 15 , and sun gear 12 , respectively.
- An arrangement where the planet carrier is connected to the crankshaft, and ring gear is connected to the output device is also possible, but the system still has to satisfy Equation (1).
- the torque of modulating device 24 is lowered (e.g. if the modulating device is a hydraulic pump, by reducing the discharge pressure or volume of the pump). This will cause sun gear 12 to spin in the direction opposite of ring gear 1 and planet carrier 2 .
- the correlation of the rotational speeds of cover 14 , sun gear 12 and output device 15 are given in Equation (1).
- Output device 15 may also be sped up above the synchronous speed by driving sun gear 12 in the same direction of rotation as ring gear 1 and planet carrier 2 .
- modulating device 24 must act as a motor, where motive power may be provided from an external source (not shown).
- the correlation of the rotational speeds of cover 14 , sun gear 12 and output device 15 are given in Equation (1).
- N ring and N pinion are the numbers of teeth on a ring gear and a pinion, respectively
- W in , W out and W ecc are the rotational speeds of a input crankshaft, an output device, and an eccentric shaft, respectively.
- an “in-line” torque transmission system can be achieved (such as between an engine and gearbox in a vehicle), in which case a “hollow” sun gear must be used.
- the planet carrier will be connected to an output shaft, which will pass through the hollow sun gear and will connect to the driven equipment.
Abstract
Description
- This application claims priority to, and incorporates by reference in its entirety, U.S. provisional application No. 61/055,866 filed 23 May 2008.
- This invention relates to power transmission devices and, more particularly, to clutching devices that can achieve torque modulation and/or speed trimming, by manipulating only a fraction of torque transferred, but over a wider speed range.
- In automotive and various industrial applications, it is often necessary to provide a clutching/speed-trimming device that is used to connect or disconnect a prime mover to or from the rest of a powertrain and/or auxiliary devices. It is also often important to be able to continuously change the speed-ratio between the prime-mover and the driven equipment, whether they are main propulsion or powertrain devices, or auxiliary devices such as, but not limited to, cooling fans, pumps, compressors and the like. Ideally, the speed ratio can be changed while the system is running and without interrupting the torque path. These functions are particularly important, but not limited to, applications where an internal combustion engine is the prime mover. The process of connecting the torque path is typically referred to as “clutching” while the process of interrupting the torque path is typically referred to as “de clutching.” The process of changing the speed ratio between the prime mover and auxiliary devices may be referred to as “speed trimming” or “speed modulation.”
- Most conventional clutching devices utilize either friction (e.g. mechanical clutches) or hydraulics (e.g. fluid couplings and torque converters) in order to establish and interrupt the torque path. Magnetic clutches and couplings are gaining in popularity especially in certain industrial application but their more widespread application is limited by cost and envelope size compared to frictional and hydraulic assemblies.
- During clutch engagement, the rotational speed of the driven equipment is gradually increased from zero, or another finite rotational speed lower than the rotational speed of the prime mover, to the rotational speed of the prime mover. This process of speeding up the driven equipment is referred to as “clutch modulation.” Energy from clutch modulation in traditional clutching devices is converted into heat, which is typically released into the atmosphere. Traditional clutches therefore have limited modulating capacity and/or, in the case of hydraulic systems, rather low operating efficiency. In cases where it may be necessary to provide speed trimming and/or torque modulation for extended periods of time, yet achieve high efficiency once clutched, typically two clutching devices are used: a hydraulic unit to provide for modulation, and a friction unit to achieve full clutch engagement (e.g. lock-up torque converters) once the driven equipment is sped-up.
- Traditionally, clutching devices modulate the entire working torque over a speed range equal to the difference between the speed of the prime mover and the starting speed of the process machine. Therefore, clutches have a tendency of being rather large and it is difficult to achieve and automate smooth, repeatable modulation. This is especially true with friction-based clutches because coefficient of friction may change during the modulation.
- There is a need for a clutching device that is smaller and more cost-effective than conventional, friction-based clutches. There is also a need for a clutching device capable of providing smooth, repeatable modulation, unrestricted in duration, and easy to automate regardless of operating conditions. Furthermore, there is a need for a clutching device capable of converting the energy of clutch modulation into an energy form that can be readily recovered and/or reintroduced into the system to provide improved efficiency of the system even when the clutch is modulating for extended periods of time.
- In one aspect, the invention provides a clutching device that includes a planetary gear set connected to a prime mover. The planetary gear set includes a ring gear, a planet carrier with at least one planet and one sun gear disposed in the planet carrier the said planet gear engaged at one side with the ring gear, and at the other side with the sun gear. The device further includes a modulating device connected to the sun gear, and an output device connected to the planet carrier. Speed modulation between the prime mover and the output device is controlled by controlling the speed of rotation of the sun gear. Energy from the speed modulation is recoverable by the modulating device.
- In drawings which show non-limiting embodiments of the invention:
-
FIG. 1 is a cut-out, partially exploded view of a clutching device according to one embodiment of the invention (modulating device not shown); and -
FIG. 2 is an exploded view of the embodiment shown inFIG. 1 (modulating device shown). -
-
Reference number Part 1 ring gear 2 planet carrier 3 planet gear 4 planet pin 5 bearing 6 spacer 7 retaining ring 8 spring pin 9 bearing 10 bearing 11 spacer 12 sun gear 13 plate 14 cover 15 output device 16 O-ring 17 O- ring 18 lock washer 19 cap screw 20 seal 21 bearing 22 bearing holder 23 pump plate 24 pump 25 splined collar 26 spacer 27 dowel 100 clutching device - Throughout the following description, specific details are set forth in order to provide a more thorough understanding of the invention. However, the invention may be practiced without these particulars. In other instances, well known elements have not been shown or described in detail to avoid unnecessarily obscuring the invention. Accordingly, the specification and drawings are to be regarded in an illustrative, rather than a restrictive, sense.
- Also, for reasons of simplicity and clarity of explanation, the following description will focus on clutching devices for driving auxiliary equipment. It will be appreciated, however, that the clutching devices and underlying principals described herein can be applied in a variety of different industrial, marine, and other applications including the main drive of propulsion systems.
-
FIGS. 1 and 2 show a clutching device according to one embodiment of the present invention.Clutching device 100 has acover 14 connected to the front-end of an engine crankshaft (not shown) by means of an adapter (also not shown).Cover 14 is the input ofclutching device 100, and is connected toring gear 1.Ring gear 1 is engaged withplanet gears 3.Planet gears 3 are mounted inplanet carrier 2 by means ofbearings 5 andpins 4, and are also engaged withsun gear 12. Anoutput device 15 is rigidly connected toplanet carrier 2 and is the output of the assembly.Output device 15 may, for example, be a sheave or a sprocket.Output device 15 drives auxiliary equipment such as cooling fans, generators, pumps, compressors and the like. Whereoutput device 15 drives the main drive of propulsion systems,output device 15 may be a shaft, for example. - Sun
gear 12 is connected to a modulating device 24 used to provide the control (reaction) torque for torque modulation. Modulating device 24 may, for example, be a hydraulic pump, a hydraulic motor, an electrical generator, an electrical motor, a friction clutch, a hydraulic coupling device, a magnetic coupling device, or the like. - Rotational power of the crankshaft is transferred to
output device 15 such that in operation, the correlation of the rotational speeds ofcover 14,sun gear 12 andoutput device 15 satisfy the following equation: -
(N ring /N sun)*W in=(1+N ring /N sun)*W out −W sun (1) - where Nring and Nsun are the numbers of teeth on
ring gear 1 andsun gear 12, respectively, and Win, Wout and Wsun are the rotational speeds ofcover 14,output device 15, andsun gear 12, respectively. An arrangement where the planet carrier is connected to the crankshaft, and ring gear is connected to the output device is also possible, but the system still has to satisfy Equation (1). - When
sun gear 12 is held stationary,output device 15 will be at “synchronous” speed that satisfies the equation: -
W out-sync =N ring/(N sun +N ring)*W in (2) - In order to slow
output device 15 below the synchronous speed, the torque of modulating device 24 is lowered (e.g. if the modulating device is a hydraulic pump, by reducing the discharge pressure or volume of the pump). This will causesun gear 12 to spin in the direction opposite ofring gear 1 andplanet carrier 2. The correlation of the rotational speeds ofcover 14,sun gear 12 andoutput device 15 are given in Equation (1). -
Output device 15 may also be sped up above the synchronous speed by drivingsun gear 12 in the same direction of rotation asring gear 1 andplanet carrier 2. To achieve this, modulating device 24 must act as a motor, where motive power may be provided from an external source (not shown). Again, the correlation of the rotational speeds ofcover 14,sun gear 12 andoutput device 15 are given in Equation (1). - Those skilled in the art will understand that the foregoing examples of epicyclical gear systems may be substituted with a cycloidal (orbital) gear systems in which case the rotational speeds have to satisfy the following equation:
-
N ring *W in =N pinion *W out +W ecc (3) - where Nring and Npinion are the numbers of teeth on a ring gear and a pinion, respectively, and Win, Wout and Wecc are the rotational speeds of a input crankshaft, an output device, and an eccentric shaft, respectively.
- Those skilled in the arts will also understand that, if and where appropriate, and that in the case of an orbital arrangement, multiple, axially split pinions may be used for better balance of the clutching device. Also, in cases where the modulation energy is limited, but smoothness of operation and cost are important, a hydraulic pump may be substituted with a friction clutch.
- Finally, those skilled in the arts will understand that an “in-line” torque transmission system can be achieved (such as between an engine and gearbox in a vehicle), in which case a “hollow” sun gear must be used. In this case the planet carrier will be connected to an output shaft, which will pass through the hollow sun gear and will connect to the driven equipment.
- As will be apparent to those skilled in the art in the light of the foregoing disclosure, many alterations and modifications are possible in the practice of this invention without departing from the spirit or scope thereof.
Claims (11)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US12/470,045 US8133147B2 (en) | 2008-05-23 | 2009-05-21 | Clutch |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US5586608P | 2008-05-23 | 2008-05-23 | |
US12/470,045 US8133147B2 (en) | 2008-05-23 | 2009-05-21 | Clutch |
Publications (2)
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US20090291799A1 true US20090291799A1 (en) | 2009-11-26 |
US8133147B2 US8133147B2 (en) | 2012-03-13 |
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US12/470,045 Active 2030-02-19 US8133147B2 (en) | 2008-05-23 | 2009-05-21 | Clutch |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102644714A (en) * | 2012-04-19 | 2012-08-22 | 燕山大学 | Continuous variable phase transmission mechanism of interruptable homodromous variable speed planetary gear trains |
USD822086S1 (en) * | 2016-01-15 | 2018-07-03 | Nabtesco Corporation | Reduction gear |
US10247279B2 (en) * | 2014-01-17 | 2019-04-02 | Drillform Technical Services Ltd. | Integrated roller-gearbox for spinner wrench |
US11835117B2 (en) * | 2016-07-08 | 2023-12-05 | Nuovo Pignone Tecnologie—SRL | Variable speed transmission and system using same |
Families Citing this family (7)
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US8481871B2 (en) | 2007-09-13 | 2013-07-09 | Raf Technology, Inc. | Dynamic thickness adaptation for an in-line scale |
US8153911B2 (en) | 2008-10-01 | 2012-04-10 | Raf Technology, Inc. | Dynamically weighing mail pieces in real time within an automated destination bar code sorter machine by temporarily accelerating the mail piece and capturing resulting closed loop motor torque sample data |
US9018544B2 (en) * | 2007-09-13 | 2015-04-28 | Raf Technology, Inc. | In-line conveyor scale with a primary first motor to provide constant torque, a secondary servo motor to provide fine-grained variable torque in response to a closed loop torque sensor, and a processor to assertain weight of an item conveved based on the closed loop servo motor response |
US9091585B2 (en) | 2013-02-08 | 2015-07-28 | Raf Technology, Inc. | Smart phone scale that uses the built-in barometric pressure sensor or orientation sensors to calculate weight |
US9564849B2 (en) | 2013-05-06 | 2017-02-07 | Raf Technology, Inc. | Scale for weighing flowing granular materials |
DE102014222253A1 (en) * | 2014-10-31 | 2016-05-04 | Robert Bosch Gmbh | Hand machine tool device |
WO2017079749A1 (en) | 2015-11-05 | 2017-05-11 | Raf Technology, Inc. | High speed robotic weighing system |
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---|---|---|---|---|
US3405571A (en) * | 1964-11-24 | 1968-10-15 | Mersch Georges | Phase displacement device of two shafts |
US4138907A (en) * | 1975-08-04 | 1979-02-13 | International Harvester Company | Hydromechanical transmission with overspeed limited variable drive |
US5505668A (en) * | 1994-07-29 | 1996-04-09 | Ikona Gears Limited | Gear system |
US5558173A (en) * | 1993-09-23 | 1996-09-24 | General Motors Corporation | Integrated hybrid transmission with mechanical accessory drive |
US5971880A (en) * | 1998-08-07 | 1999-10-26 | Keiser; Fred | Infinitely variable ratio transmission |
US6801842B2 (en) * | 2001-04-10 | 2004-10-05 | Denso Corporation | Accessory equipment driving device for vehicle |
US7101307B2 (en) * | 2003-07-14 | 2006-09-05 | Luke W. Clauson | Methods and devices for altering the transmission ratio of a drive system |
US20080039263A1 (en) * | 2006-08-14 | 2008-02-14 | Usoro Patrick B | Starter alternator accessory drive system for a hybrid vehicle |
-
2009
- 2009-05-21 US US12/470,045 patent/US8133147B2/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3405571A (en) * | 1964-11-24 | 1968-10-15 | Mersch Georges | Phase displacement device of two shafts |
US4138907A (en) * | 1975-08-04 | 1979-02-13 | International Harvester Company | Hydromechanical transmission with overspeed limited variable drive |
US5558173A (en) * | 1993-09-23 | 1996-09-24 | General Motors Corporation | Integrated hybrid transmission with mechanical accessory drive |
US5505668A (en) * | 1994-07-29 | 1996-04-09 | Ikona Gears Limited | Gear system |
US5971880A (en) * | 1998-08-07 | 1999-10-26 | Keiser; Fred | Infinitely variable ratio transmission |
US6801842B2 (en) * | 2001-04-10 | 2004-10-05 | Denso Corporation | Accessory equipment driving device for vehicle |
US7101307B2 (en) * | 2003-07-14 | 2006-09-05 | Luke W. Clauson | Methods and devices for altering the transmission ratio of a drive system |
US20080039263A1 (en) * | 2006-08-14 | 2008-02-14 | Usoro Patrick B | Starter alternator accessory drive system for a hybrid vehicle |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102644714A (en) * | 2012-04-19 | 2012-08-22 | 燕山大学 | Continuous variable phase transmission mechanism of interruptable homodromous variable speed planetary gear trains |
US10247279B2 (en) * | 2014-01-17 | 2019-04-02 | Drillform Technical Services Ltd. | Integrated roller-gearbox for spinner wrench |
USD822086S1 (en) * | 2016-01-15 | 2018-07-03 | Nabtesco Corporation | Reduction gear |
US11835117B2 (en) * | 2016-07-08 | 2023-12-05 | Nuovo Pignone Tecnologie—SRL | Variable speed transmission and system using same |
Also Published As
Publication number | Publication date |
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US8133147B2 (en) | 2012-03-13 |
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